US4720929A - Trenching device - Google Patents
Trenching device Download PDFInfo
- Publication number
- US4720929A US4720929A US06/829,779 US82977986A US4720929A US 4720929 A US4720929 A US 4720929A US 82977986 A US82977986 A US 82977986A US 4720929 A US4720929 A US 4720929A
- Authority
- US
- United States
- Prior art keywords
- attached
- cutting wheel
- piston
- friction
- vehicle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/18—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
- E02F3/20—Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with tools that only loosen the material, i.e. mill-type wheels
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K25/00—Auxiliary drives
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19251—Control mechanism
- Y10T74/19256—Automatic
- Y10T74/19274—Automatic torque responsive
Definitions
- This invention pertains to trenchers, that is, motorized devices for digging trenches up to ten feet or more deep, and six feet or more wide, at a single pass. Specifically, this invention pertains to improvements in the transmission and control of power to the cutting wheel and the tracks of the trencher.
- the cutting wheel is elongated, resembling the blade of a chain saw.
- the cutting wheel is equipped with a number of buckets about its outer periphery, with each of the buckets having a number of cutting teeth. As the cutting wheel is rotated, the teeth cut into the ground, filling each of the individual buckets with the cut material.
- the buckets carry the material out of the trench and deposit their load onto a running conveyor belt which transports the material to the side of the trench. As the cutting wheel rotates, the vehicle travels ahead as fast as the material can be cut and removed from the trench.
- the operator of the trencher has control over two essential variables.
- the first is the speed at which the trencher is set to move forward.
- the typical large scale trencher is equipped with a pair of tracks which have independent controls called “crowd handles".
- the operator wants the maximum forward speed which can be obtained. This will depend upon the terrain to be traversed and the material to be trenched.
- the appropriate setting on the crowd handles is arrived at through trial and error. Once set at an optimum position, the operator prefers not to change the setting.
- the second variable is the amount of torque delivered to the cutting wheel.
- the operator strives for an optimal setting wherein the torque is sufficiently high such that the cutting wheel will not be stopped upon encountering every obstruction, but not so high, that when a truly immoveable obstruction is encountered, which does stop the cutting wheel, damage will result to the downstream components.
- twin disk over-center clutch Another device previously utilized as a tortional limiting means in large scale trenchers is the twin disk over-center clutch.
- power is transmitted to downstream components by virtue of two or more dry clutch plates which act upon one another frictionally.
- the clutch plates are brought together by means of an over center toggle arrangement which includes a fine thread adjusting collar.
- this type of device when used in a large scale trencher, has multiple disks and is located immediately aft of the digging transmission.
- the tortional requirements of the device are quite high and require substantial friction.
- the intent of the device is to limit the amount of torque which can be transmitted to downstream components, so a proper setting of the adjusting collar is critical to the proper functioning of this device.
- This device has no means for measuring the resulting friction achieved at any particular setting of the adjusting collar. Only an experienced operator, who has developed a "feel" for the device, can be expected to consistently adjust the device properly. It is not unusal for an inexperienced operator to tighten the adjusting collar too much, resulting in catastrophic failure of downstream components. Even experienced operators have failed to properly set this device.
- Another prior art device was an oil drive mechanism. Because of the problems associated with the dry twin disk over-center clutch mechanism, some people in the field have turned to a hydraulic system for power transmission, relying on release valves to protect the downstream components in the event the cutting wheel hits some immovable obstruction.
- This system is subject to three drawbacks. First, the system is sensitive to hydraulic oil contamination. As might be imagined, the trenching operation is typically a very dusty, dirty environment. Therefore, the chances of contamination are enhanced greatly. Second, on large scale equipment, the system becomes quite complex with as many as four pumps, four motors and associated components necessary to transmit the desired power. The failure at any point of this complex system is a failure of the entire system.
- any failure is extremely time consuming because of the difficulty in diagnosis, and the extensive nature of repairs. Often, hydraulic repairs can not be effected in the field, and require that the components be returned to the shop. Moreover, any repairs in the field entail opening the system to the harsh environment, leading to further contamination and further failures.
- the prior art devices have also not provided for immediate release when an obstruction which causes the cutting wheel to stop is encountered. Even though the devices may slip as designed, the slippage still places a tremendously increased load on the downstream drive train. Unless immediately released, damage may occur. At a minimum, this increases wear and tear on the other components, leading to more frequent repair. In the past, with prior art devices, equipment failure once a week or more is not unusual.
- This invention provides such an improved trencher by incorporating a novel system for the transmission and limiting of torque to the cutting wheel, for adjustment of the tortional setting of the system, for protection of the drive train in the event the cutting wheel encounters an immoveable obstruction, and for neutralizing the forward motion of the tracks of the trencher when an immoveable obstruction is encountered.
- clutches are designed to grab and hold unless completely released.
- brake mechanisms are designed for slippage.
- the material on the clutch plates is designed such that the coefficient of friction increases in the dynamic state; whereas, in the traditional brake mechanism, the brake pads are equipped with a material designed to have a reduced coefficient of friction in the dynamic state, compared with the static state.
- the friction discs are equipped with a material providing for reduced coefficient of friction in a dynamic state.
- the torque to which downstream components are subjected is immediately reduced by up to forty percent.
- the friction discs are oil cooled, and have semi-circular grooves in each phase for increased cooling.
- the amount of compression to which the friction discs are subjected is determined by a fluid activated piston which acts upon the friction discs and their associated reaction plates. As the fluid pressure in the piston chamber is increased, the piston applies more force thereby increasing friction. This pressure is monitored and adjusted by the operator by a system of controls in the cab.
- a novel system which includes controls for monitoring, adjusting and releasing pressure on the piston.
- One of these controls is a pedal valve by which the operator of the trencher can quickly disengage the friction discs from the reaction plates by relieving all presure on the piston.
- the system also includes a pressure differential switch which senses a drop in pressure across a pedal valve. The switch opens a solenoid valve which vents the hydraulic pumps which move the tracks of the trencher in the forward direction. In essence, this puts the tracks of the trencher into a neutral gear and releases the forward pressure on the cutting wheel. In operation, this causes the trencher to "step back", releasing the cutting wheel from the obstruction. This is done instantaneously when the operator depresses the pedal valve fully.
- FIG. 1 is a side view of a typical trencher.
- FIG. 2 is a cross-sectional view of the torsional limiting device. To show greater detail, this figure has been bifurcated along the device's center line, with the upper portion being shown in FIG. 2A, the lower portion being shown in FIG. 2B.
- FIG. 3 is a schematic of the control system by which the torsion limiting devise is monitored, adjusted and released and by which the tracks of the trencher are neutralized.
- FIG. 4 is a side view of one of the friction discs in the torsional limiting device.
- FIG. 5 is a cross section of one of the discs.
- the preferred trencher will have an engine compartment 10, an enclosed cab 12, a track system 14, and a hydraulically adjusted boom assembly 16, to which the cutting wheel 18 and the rider shoe 20 are attached.
- the cutting wheel 18 is equipped with a number of buckets 22 around its outer periphery. Each of the buckets 22 has several cutting teeth 24 at the leading edge thereof.
- the power plant 26 housed within engine compartment 10 should be of sufficient power output to turn the track system 14, the cutting wheel 18 and the conveyor belt 38.
- Power plants available from Caterpillar such as its unit 3408TA, or smaller, depending upon the size of the trencher, have proven reliable.
- standard Caterpillar unit 988 has proven reliable as transmission 28.
- Anterior of transmission 28 is the torsional limiting device 30 which will be described in detail infra.
- the power output from device 30 is attached to drive train 32.
- the drive train 32 turns the sprocket and chain assembly 34 which in turn drives a sprocket wheel (not shown) which engages the rim gear 36 on the interior periphery of cutting wheel 18.
- all components downstream of the device 30 are positive drive allowing for no slippage whatsoever. As will be discussed in greater detail, all protection for the equipment is provided by device 30.
- FIGS. 2A and B the interior workings of device 30 are shown in detail.
- FIG. 2A is the top half
- FIG. 2B is the bottom half
- FIG. 2 has been bifurcated along the center line of the device 30 in order to show greater detail.
- device 30 has been adapted for use on standard Caterpillar transmission 988 and the adaptor housing 40 has been designed and constructed for that purpose. It should be understood, however, that this device 30 could be adapted for use with any transmission, with the adaptor housing 40 being modified to accommodate same.
- a drive flange 42 is splined to the drive shaft 44 which exits from the transmission 28.
- Ball bearing assembly 46 which is retained in position by snap rings 48 and 50, is provided for centering and friction reduction.
- a carrier ring/ring seal assembly 52 surrounds drive flange 42 to seal against leakage of lubricating fluid.
- the ball bearing assembly 46 and the carrier ring/ring seal assembly 52 are secured by dowels 54 and 56, respectively.
- Hub coupling 58 is attached to drive flange 42 by means of dowel pins 60. Bolts (not shown) are also used at spaced intervals around the periphery of the coupling. Hub coupling 58 engages the exterior gear teeth on sun gear 62. Snap ring 64 holds sun gear 62 in position on hub coupling 58.
- the sun gear 62 engages planet gear 66 which rotates on bearings 68 on shaft 70, between discs 72, all of which is carried on planet carrier 74.
- Pin 71 holds shaft 70 in place; and internal ports 73 provide for interior lubrication of bearing 68 and discs 72.
- the planet gear 66 in turn engages ring gear 76 which has gear teeth about its interior periphery and is externally splined.
- a series of friction discs 78 are slidably splined to ring gear 76 and which are attached perpendicularly to the direction of travel of ring gear 76.
- a reaction plate 82 Placed in between each adjacent pair of disc plates 78 is a reaction plate 82.
- Reaction plates 82 are slidably keyed to dowel pins 95 on piston housing 86.
- Piston housing 86 is attached to the adapter housing 40 by dowel pins 87, and is attached to rear cover plate by means of bolts 91.
- Each friction disc 78 comprises an inner-ring to which friction material 79 is attached on either side thereof.
- the friction material used has a higher coefficient of friction in the static state than in the dynamic state, so that when the discs 78 begin to move relative to reaction plates 82, the friction between them reduces.
- Caterpillar has produced a special disc for this purpose. It has been assigned Special Caterpillar Part No. 9W2152.
- the friction material 79 has grooves 81 formed in both faces thereof. The grooves 81 radiate from the interior edge to the exterior edge of the disc in a criss-cross fashion. These grooves 81 provide passageways between discs 78 and reaction plates 82 for the cooling fluid.
- Piston 88 which resides in piston housing 86, is responsive to fluid pressure administered through port 81.
- pneumatic pressure is used.
- a pair of ring seals 90 and 92 abut against piston chamber 94 in piston housing 86 to prevent pressure loss.
- Piston 88 is biased away from the friction discs 78 by means of springs 93, which is inserted between dowel pins 95, and at one end abuts and acts upon spring plate 97 which is part of piston 88, and at its other end, abuts and acts upon rear cover plate 89.
- One end of dowel pin 95 resides within an appropriately-sized aperture in piston housing 86; the other end in an appropriately sized aperture in cover plate 89.
- Dowel pins 95 are inserted through a hole in spring plate 97.
- Rotation of the planet carrier 74 is delivered exteriorly of device 30 via end yoke 98 to which carrier 74 is splined.
- End yoke 98, and hence planet carrier 74 are journalled on roller bearing assembly 96, which is held in position at one end by plate 100 attached to end yoke 98 by means of bolt 102, and at the other end by retainer plate 104, which is attached to the rear cover 89 by means of bolt 108.
- O-ring 109 seals against fluid leakage between retainer plate 104 and rear cover 89.
- a large ring seal 110 resides within an appropriately sized groove in retainer plate 104 to provide sealing contact against end yoke 98 to prevent fluid leakage.
- a capture plate 112 is held in place in the interior cavity of planet carrier 74 by means of snap ring 114.
- Spline lubrication hole 116 is provided in capture plate 112.
- a slot 113 is provided in end cap 118 for communicating lubrication oil to end yoke 98 and planet carrier 74.
- An end cap 118 is attached to capture plate 112 by means of bolt 120.
- An O-ring seal 122 resides within an appropriately sized groove in end cap 118 to seal against end yoke 98 to preclude fluid drainage.
- a snap ring 124 also assists in keeping the capture plate 112 and end cap 118 in position. End yoke 98 is available for linkage to the drive train 32.
- the device 30 is completed by outer housing 126 which is attached between the adapter housing 40 and the cover plate 89 by means of bolts 128 and 130, and dowel pins 132. Interior ports 140 are provided for communication of lubrication fluid throughout the device 30. A cooling oil pressure port 142 is provided in rear cover 89 near the bottom of the mechanism and guage 158 is attached thereto.
- the device 30, and specifically the friction discs 78 and reaction plates 82 are oil cooled.
- a pump (not shown) is powered off of engine 26. The pump transports oil from the lubrication reservoir 150 and presents it through port 152 into chamber 154. This oil is forced between friction discs 78 and reaction plates 82 through grooves 81 and is returned to tank 150 through port 156. As the friction material 79 is worn off friction discs 78, the grooves 81 decrease in size, resulting in increased pressure in chamber 154. This pressure is recorded on gauge 158. It has been found that when the pressure on gauge 158 reads 30 psi, replacement of the friction material 79 is needed.
- FIG. 3 The system for supplying, controlling, adjusting and releasing the pressure acting on piston 88 in device 30 and neutralizing the tracks 14 of the trencher is shown schematically in FIG. 3.
- Air is pressurized via compressor 162, dried by drier 160, and stored in tanks 164.
- a gauge for the system pressure 166 is located in cab 12 for monitoring by the operator of the trencher.
- An auxillary system 168 can be provided.
- the pressurized air from the tanks 164 is delivered to the device 30 through a series of controls which allow the operator of the trencher to precisely adjust the amount of friction between the friction discs 78 and reaction plates 82.
- a safety pressure regulator 170 is provided to insure that no more pressure than can be safely utilized at piston 88 is presented to chamber 94, and hence, to prevent excessive torque from being transmitted to downstream components.
- the air passes through a pressure regulating control unit 172 which is located in the cab 12. Pressure control unit 172 can be manually adjusted by the operator to set the maximum pressure the operator wants delivered to piston 88, but only up to the maximum allowed by regulator 170.
- Pedal valve 174 allows the operator to "feather" the pressure being delivered to the piston 88.
- a pressure differential switch 176 monitors the pressure fore and aft of the pedal valve 174, and is set to trigger a solenoid valve which in turn vents the track pumps 177 which has the effect of stopping the forward motion of the tracks, essentially putting the tracks in "neutral". The pumps are again pressurized when the pedal valve 174 is released.
- a clutch on/off valve 178 and a quick release valve 180 are also provided in cab 12 for the operator.
- the regulator 170 should be set at 90 psi approximately, with the pressure control unit 172 set at 80 psi maximum.
- the pressure differential switch 176 should be set to trigger at a 30 psi differential.
- the maximum pressure applied to piston 88, and hence to the tensioning of device 30, can be controlled, monitored and adjusted minutely and easily by the operator from the enclosed cab 12 of the trencher.
- the pedal valve 174 provides the operator with the ability to instantaneously feather the pressure. In the event the cutting wheel 18 encounters an immovable object, the operator can immediately release all pressure on piston 88 by depressing pedal valve 174 completely, or triggering clutch on/off valve 178 and subsequently the quick release valve 180.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims (10)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/829,779 US4720929A (en) | 1986-02-14 | 1986-02-14 | Trenching device |
EP87307591A EP0304522A1 (en) | 1986-02-14 | 1987-08-27 | Improved trenching device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/829,779 US4720929A (en) | 1986-02-14 | 1986-02-14 | Trenching device |
Publications (1)
Publication Number | Publication Date |
---|---|
US4720929A true US4720929A (en) | 1988-01-26 |
Family
ID=25255534
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US06/829,779 Expired - Lifetime US4720929A (en) | 1986-02-14 | 1986-02-14 | Trenching device |
Country Status (2)
Country | Link |
---|---|
US (1) | US4720929A (en) |
EP (1) | EP0304522A1 (en) |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5437509A (en) * | 1993-11-18 | 1995-08-01 | James C. Casey | Bearing and seal assembly for trencher endless chain drives |
US5471771A (en) * | 1994-06-10 | 1995-12-05 | Gilbert; Jerry F. | Method and apparatus for cooling chain type diggers |
US5911292A (en) * | 1996-05-04 | 1999-06-15 | Schuler Pressen Gmbh & Co. | High efficiency torque transmission arrangement with radial coolant flow |
US5921361A (en) * | 1997-07-24 | 1999-07-13 | Midwest Brake Bond Company | Press drive with oil shear clutch/brake drives |
US6193440B1 (en) | 1999-02-26 | 2001-02-27 | Kenneth A. Pidgeon | Railroad cable plow apparatus |
US6305515B1 (en) * | 1999-07-20 | 2001-10-23 | Power Transmission Technology, Inc. | Hydraulically actuated power takeoff clutch assembly |
US20030183474A1 (en) * | 2001-06-22 | 2003-10-02 | Power Transmission Technology, Inc. | Compact dry power takeoff unit |
US20090263195A1 (en) * | 2008-04-16 | 2009-10-22 | Jeff Horan | Trenching and drain installation system and method |
US20110072692A1 (en) * | 2009-05-22 | 2011-03-31 | Loram Maintenance Of Way, Inc. | Rotary undercutter for rail line maintenance |
CN103216541A (en) * | 2012-01-19 | 2013-07-24 | 株式会社捷太格特 | Clutch plate and method of producing same |
US10024459B1 (en) * | 2015-04-02 | 2018-07-17 | Ag Leader Technology, Inc. | Tile feed wheel control |
CN111706251A (en) * | 2020-07-09 | 2020-09-25 | 广州大学 | Stone chiseling and ditching all-in-one machine |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2351331B (en) * | 1996-06-27 | 2001-02-14 | Midwest Brake Bond Co | A clutch assembly |
Citations (11)
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---|---|---|---|---|
US2084887A (en) * | 1936-03-23 | 1937-06-22 | Buckeye Traction Ditcher Co | Power transmission means |
US2708800A (en) * | 1949-08-15 | 1955-05-24 | Pettibone Mulliken Corp | Loader-crowding drive |
US2894341A (en) * | 1953-10-05 | 1959-07-14 | William M Amthor | Digging machine |
US3251439A (en) * | 1964-01-17 | 1966-05-17 | Glenn T Randol | Torque-responsive clutch mechanism for detecting initial plate contact |
US3945138A (en) * | 1972-06-16 | 1976-03-23 | Orenstein & Koppel Aktiengesellschaft | Hydraulically controlled and driven bucket wheel dredge |
US3970154A (en) * | 1973-03-20 | 1976-07-20 | Banister Pipelines, Ltd. | Tool power system usable as substitute for vehicle propulsion |
US4458793A (en) * | 1980-12-18 | 1984-07-10 | Fichtel & Sachs Ag | Hydraulic clutch brake for wet plate clutches |
US4488626A (en) * | 1981-08-06 | 1984-12-18 | Handke Kenneth E | Torque transmitting apparatus and method |
US4516655A (en) * | 1983-08-12 | 1985-05-14 | The Gradall Company | Remote drive with powershift transmission |
US4529073A (en) * | 1982-09-30 | 1985-07-16 | Deere & Company | Cooling oil cut-off valve for a clutch |
US4574926A (en) * | 1983-06-28 | 1986-03-11 | John Bubak | Oil cooled and fluid pressure operated clutch assembly |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
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US2810304A (en) * | 1952-09-18 | 1957-10-22 | Joy Mfg Co | Apparatus for controlling the transmission of torque |
US2782535A (en) * | 1953-09-28 | 1957-02-26 | Fullerform Inc | Ditching machine |
US2863335A (en) * | 1955-05-10 | 1958-12-09 | Jack & Heintz Inc | Torque limiter |
US3421235A (en) * | 1965-07-21 | 1969-01-14 | Cleveland Trencher Co | Excavating machine |
US4004641A (en) * | 1975-02-24 | 1977-01-25 | Caterpillar Tractor Co. | Motor grader drawbar assembly with safety clutch mechanism |
US4114477A (en) * | 1976-10-18 | 1978-09-19 | Iverson Roger A | Reversible power transmission |
DE3248084A1 (en) * | 1982-12-24 | 1984-06-28 | Gewerkschaft Eisenhütte Westfalia, 4670 Lünen | TRANSMISSION WITH OVERLOAD PROTECTION, ESPECIALLY FOR THE DRIVE OF CARBON PLANES AND THE LIKE |
-
1986
- 1986-02-14 US US06/829,779 patent/US4720929A/en not_active Expired - Lifetime
-
1987
- 1987-08-27 EP EP87307591A patent/EP0304522A1/en not_active Withdrawn
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2084887A (en) * | 1936-03-23 | 1937-06-22 | Buckeye Traction Ditcher Co | Power transmission means |
US2708800A (en) * | 1949-08-15 | 1955-05-24 | Pettibone Mulliken Corp | Loader-crowding drive |
US2894341A (en) * | 1953-10-05 | 1959-07-14 | William M Amthor | Digging machine |
US3251439A (en) * | 1964-01-17 | 1966-05-17 | Glenn T Randol | Torque-responsive clutch mechanism for detecting initial plate contact |
US3945138A (en) * | 1972-06-16 | 1976-03-23 | Orenstein & Koppel Aktiengesellschaft | Hydraulically controlled and driven bucket wheel dredge |
US3970154A (en) * | 1973-03-20 | 1976-07-20 | Banister Pipelines, Ltd. | Tool power system usable as substitute for vehicle propulsion |
US4458793A (en) * | 1980-12-18 | 1984-07-10 | Fichtel & Sachs Ag | Hydraulic clutch brake for wet plate clutches |
US4488626A (en) * | 1981-08-06 | 1984-12-18 | Handke Kenneth E | Torque transmitting apparatus and method |
US4529073A (en) * | 1982-09-30 | 1985-07-16 | Deere & Company | Cooling oil cut-off valve for a clutch |
US4574926A (en) * | 1983-06-28 | 1986-03-11 | John Bubak | Oil cooled and fluid pressure operated clutch assembly |
US4516655A (en) * | 1983-08-12 | 1985-05-14 | The Gradall Company | Remote drive with powershift transmission |
Cited By (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5437509A (en) * | 1993-11-18 | 1995-08-01 | James C. Casey | Bearing and seal assembly for trencher endless chain drives |
US5471771A (en) * | 1994-06-10 | 1995-12-05 | Gilbert; Jerry F. | Method and apparatus for cooling chain type diggers |
DE19617951B4 (en) * | 1996-05-04 | 2006-01-05 | Schuler Pressen Gmbh & Co. Kg | Coupling device for body presses |
US5911292A (en) * | 1996-05-04 | 1999-06-15 | Schuler Pressen Gmbh & Co. | High efficiency torque transmission arrangement with radial coolant flow |
US5921361A (en) * | 1997-07-24 | 1999-07-13 | Midwest Brake Bond Company | Press drive with oil shear clutch/brake drives |
US6193440B1 (en) | 1999-02-26 | 2001-02-27 | Kenneth A. Pidgeon | Railroad cable plow apparatus |
US6305515B1 (en) * | 1999-07-20 | 2001-10-23 | Power Transmission Technology, Inc. | Hydraulically actuated power takeoff clutch assembly |
US20030183474A1 (en) * | 2001-06-22 | 2003-10-02 | Power Transmission Technology, Inc. | Compact dry power takeoff unit |
US6874610B2 (en) * | 2001-06-22 | 2005-04-05 | Power Transmission Technology, Inc. | Compact dry power takeoff unit |
US8157477B2 (en) * | 2008-04-16 | 2012-04-17 | Aurora Sun Alliance Corp. | Trenching and drain installation system and method |
US20090263195A1 (en) * | 2008-04-16 | 2009-10-22 | Jeff Horan | Trenching and drain installation system and method |
US20110072692A1 (en) * | 2009-05-22 | 2011-03-31 | Loram Maintenance Of Way, Inc. | Rotary undercutter for rail line maintenance |
US7987620B2 (en) * | 2009-05-22 | 2011-08-02 | Loram Maintenance Of Way, Inc. | Rotary undercutter for rail line maintenance |
CN103216541A (en) * | 2012-01-19 | 2013-07-24 | 株式会社捷太格特 | Clutch plate and method of producing same |
US20130186727A1 (en) * | 2012-01-19 | 2013-07-25 | Nhk Spring Co., Ltd. | Clutch plate and method of producing same |
US9206860B2 (en) * | 2012-01-19 | 2015-12-08 | Jtekt Corporation | Clutch plate and method of producing same |
CN103216541B (en) * | 2012-01-19 | 2017-08-04 | 株式会社捷太格特 | Clutch plate and the method for manufacturing clutch plate |
US10024459B1 (en) * | 2015-04-02 | 2018-07-17 | Ag Leader Technology, Inc. | Tile feed wheel control |
CN111706251A (en) * | 2020-07-09 | 2020-09-25 | 广州大学 | Stone chiseling and ditching all-in-one machine |
Also Published As
Publication number | Publication date |
---|---|
EP0304522A1 (en) | 1989-03-01 |
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